Clutch disk arrangement for a multi-disk clutch

ABSTRACT

A clutch disk arrangement for a multi-disk clutch includes a hub element connectable to a shaft for rotation with the shaft about an axis of rotation. A carrier arrangement has a first carrier element and a second carrier element. The first carrier element is connected to the hub so that the first carrier element rotates with the hub. The second carrier element is connected to the first carrier element such that it is foxed with respect to rotation and axially movable relative to the first carrier element. The clutch disk arrangement further comprises at least two friction lining units. On of the friction lining units is firmly connected to the first carrier element and a second one of the friction elements is firmly connected to the second carrier element. Accordingly, the friction lining units are fixed with respect to rotation and axially movable relative to the hub element via the carrier arrangement.

CROSS-REFERENCE TO RELATED APPLICATION(S)

This application is a Divisional of U.S. patent application Ser. No.09/573,248, filed May 18, 2000 now U.S. Pat. No. 6,523,662, which claimspriority from Applications filed in Germany on May 19, 1999, No. 199 22874.4, and on Dec. 24, 1999, No. 199 63 023.2.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a clutch disk arrangement for amulti-disk clutch having a hub element fixedly connectable with respectto rotation to a shaft, a carrier arrangement fixedly connected withrespect to rotation to the hub, and two friction linings connected tothe hub via the carrier arrangement such that the two friction liningsare fixed with respect to rotation and axially moveable relative to thehub element.

2. Description of the Related Art

A clutch disk arrangement having two friction lining units is disclosedin German reference DE-A 24 60 963. A first one of the two frictionlining units is connected firmly to a hub via a torsional vibrationdamper. A carrier part is also firmly connected to the hub by thetorsional vibration damper. A second one of the two friction liningunits is connected to the carrier part so that it is fixed with respectto rotation and axially movable.

Another clutch disk arrangement comprising a multi-disk clutch with afriction lining unit carrier is disclosed in German reference DE-A 20 52899. The friction lining carrier of this device comprises a solidcomponent connected firmly to a hub via a torsional vibration damper.This carrier has an essentially T-shaped sectional contour. The radiallyouter region of the carrier is connected to a plurality of frictionlining units such that the plural friction lining units are fixed withrespect to rotation and axially movable relative to said carrier. Aproblem with this carrier is that due to its T-shaped sectional contour,the carrier must be formed in a casting process or by machining which isa relatively expensive operation.

SUMMARY OF THE INVENTION

The object of the present invention is to provide a clutch diskarrangement for a multi-disk clutch which is simple to construct and maybe used for a variety of different clutch disk arrangements.

According to an embodiment of the present invention, the object isachieved by a clutch disk arrangement for a multi-disk clutch having ahub element fixedly connectable to a shaft with respect to relativerotation, a carrier arrangement connected to the hub, and at least twofriction lining units fixed with respect to rotation relative to thecarrier arrangement such that friction linings are connected to the hubvia the carrier arrangement.

The carrier arrangement further comprises a first carrier element and asecond carrier element, wherein the first carrier element is fixedlyconnected with respect to rotation and axially movable relative to thesecond carrier element. The first carrier element is connected to thehub element and is connected to a first one of the at least two frictionlining elements. A second one of the at least two friction lining unitsis firmly connected to the second carrier element.

This configuration of a clutch disk arrangement for a multi-disk clutchaccording to an embodiment of the present invention ensures that theaxial relative motion between the individual friction lining unitsrequired for carrying out clutch engagement and disengagement operationsis separated in terms of design from the friction lining units and istransferred to the region of the carrier elements. That is, the frictionlining units are not required to be designed for this function of therequired axial relative motion. This allows these design areas to beoptimized in accordance with the relevant operating requirements therebyincreasing the operating reliability and simplifying the constructionand contributing to a reduction in costs. In addition, this modularconfiguration allows adaptation to a very wide variety of clutchconfigurations simply by replacing various modular areas by othermodular areas.

For example, the first carrier element may comprise a first engagementformation projecting substantially radially outward and the secondcarrier element may have a second engagement formation projectingsubstantially radially inward and in meshed engagement with the firstengagement formation. This engagement may, for example, be achieved ifthe first engagement formation comprises a longitudinally extendingexternal toothing and the second engagement formation comprises alongitudinally extending internal toothing. To minimize cost and spacerequirements, at least one of the first and second carrier elements maycomprise a substantially cup-shaped design having a cup base region anda circumferential wall region.

The substantially cup-shaped configuration of at least one of the firstand second carrier elements allows a functional separation betweenvarious areas. For example, if the first and second carrier elementshave a cup-shaped design, the friction lining units may be fixed ontorespective base regions of the first and second carrier elements and thefirst and second engagement formations may be formed in thecircumferential wall regions of the first and second carrier element.Accordingly, the axial mobility of the friction lining units is effectedby the axially movable connection between the first and second carrierswhich is functionally separate from the friction lining units.

In the above configuration of the clutch disk arrangement according tothe embodiment of the present invention, the first and/or the secondcarrier element may be formed by a forming operation such, for example,as a press forming operation from a sheet-metal blank. The simpleformation operation contributes considerably to a low overall cost forthe a clutch disk arrangement according to the present invention.

The clutch disk arrangement according to the present invention is alsosuitable for use with multi-disk clutches which have more than twofriction lining units. For this purpose, the second carrier elementhaving the second engagement formation may comprise a third engagementformation projecting substantially radially outward for engagement of atleast one further friction lining unit to this carrier element in amanner which prevents relative rotation and allows axial movement.

This connection may be achieved if the third engagement formation isformed by or during the integral formation of the second engagementformation. In the clutch disk arrangement according to the presentinvention, one of the carrier elements is preferably fixedly connectedto the hub element. Therefore, axial movement of the friction liningunit connected to that carrier element that is connected to the hub iseffected by axial movement of the hub.

According to a further embodiment of the present invention, the objectof the present invention is achieved by a clutch disk arrangementcomprising a carrier arrangement having a carrier element with acup-shaped design which is connected to the hub element.

In this embodiment, the carrier element further comprises acircumferential wall region with an engagement formation with whichrespective counterengagement formations on the friction lining unitsengage. The engagement between the carrier element and the frictionlining units prevents relative rotation and allows relative axialdisplacement. The engagement formation of the carrier element preferablycomprises an external toothing which extends longitudinally along thedirection of the axis of rotation.

In this embodiment production costs may be minimized if the carrierelement is produced in a forming operation such, for example, as a pressforming operation from a sheet-metal blank.

To obtain rotational coupling of the friction lining units to thecarrier element, each of the friction lining units comprises at leastone lining carrier element which comprises at least one part of thecounterengagement formation. The at least one part of the counterengagement formation may comprise an engagement projection. In thepreferred embodiment, a plurality of engagement projections are arrangedon the at least one lining carrier element.

The counterengagement formation may be obtained in a simple manner if atleast one contact surface is formed on at least one engagementprojection by bending a tab-like extension provided on the engagementprojection.

In a further embodiment of the clutch disk arrangement according to theinvention, the carrier element connected to the hub element is firmlyconnected to the hub element via a torsional vibration damper.Therefore, in the context of the present invention, the expressions“connected” or “firmly connected” also includes a limited relativerotary motion or a slight relative axial motion of the variouscomponents connected to one another, due, for example, to elasticity,either of a torsional vibration damper or of materials themselves.

In this embodiment, a base region of the carrier element may beconnected to the hub element to form a central disk element of thetorsional vibration damper. Furthermore, cover disk elements may also bearranged on the hub element, on each side of the central disk elementwith at least one damping element acting between the central diskelement and the cover disk elements.

Other objects and features of the present invention will become apparentfrom the following detailed description considered in conjunction withthe accompanying drawings. It is to be understood, however, that thedrawings are designed solely for purposes of illustration and not as adefinition of the limits of the invention, for which reference should bemade to the appended claims. It should be further understood that thedrawings are not necessarily drawn to scale and that, unless otherwiseindicated, they are merely intended to conceptually illustrate thestructures and procedures described herein.

BRIEF DESCRIPTION OF THE DRAWINGS

In the drawings, wherein like reference characters denote similarelements throughout the several views:

FIG. 1 is a partial axial view of a clutch disk arrangement according toan embodiment of the present invention;

FIG. 2 is a longitudinal sectional view of the clutch disk arrangementshown in FIG. 1, along the line II—II in FIG. 1;

FIG. 3 is a perspective exploded view of the clutch disk arrangement ofFIG. 1;

FIG. 4 is a partial axial view of another embodiment of the clutch diskarrangement according to the present invention;

FIG. 5 is a longitudinal sectional view of the clutch disk arrangementshown in FIG. 4, along the line V—V in FIG. 4;

FIG. 6 is a perspective exploded view of the clutch disk arrangementillustrated in FIG. 4;

FIG. 7 is a partial sectional view of the clutch disk arrangement ofFIGS. 1-3 with a torsional vibration damper; end

FIG. 8 is a partial sectional view of another embodiment of the clutchdisk arrangement of FIGS. 1—3 with a torsional vibration damper;

FIG. 9 is a partial sectional view of the clutch disk arrangement ofFIGS. 4-6 with a torsional vibration damper; and

FIG. 10 is a partial sectional view of another embodiment of the clutchdisk arrangement of FIGS. 4-6 with a torsional vibration damper.

DETAILED DESCRIPTION OF THE PRESENTLY PREFERRED EMBODIMENTS

Referring to FIGS. 1 to 3, a clutch disk arrangement 10 according to thepresent invention for use with a multi-disk clutch comprises first andsecond friction lining units 12, 14 which, as described below, arearranged at a distance from one another in the direction of an axis ofrotation A about which the clutch disk arrangement 10 rotates when theclutch is in operation. The first and second friction lining units 12,14 are axially displaceable relative to one another in the direction ofthe axis of rotation A to allow clutch engagement and disengagementoperations.

As shown, in particular, in FIG. 3, the clutch disk arrangement 10according to the invention comprises a hub element 16. An innercircumferential surface of the hub element has a toothing 18 which isconnectable via a rotationally rigid coupling with a shaft, e.g. atransmission input shaft (not shown).

A first carrier element 20 is firmly connected to the hub element 16.FIG. 2 shows that the first carrier element 20 comprises an essentiallycup-shaped design with a cup base region 22 and a circumferential wallregion 44. A central opening 24 is arranged in the cup base region 22and is pushed onto the hub element 16 until the cup base region 22strikes axially against an annular shoulder 26 on the hub element 16.After the cup base 22 contacts the annular shoulder 26, the firstcarrier element 20 may be fixedly connected on the hub element 16 bycaulking, welding or other suitable connection. Furthermore, essentiallytriangular-shaped openings 28 are formed in the cup base region 22 forreducing the weight of the first carrier element 20. A plurality ofrivet openings 30 are provided in the region of the cup base region 22through which rivet studs 32 are passed. The first friction lining unit12 is fixed on the first carrier element 20 via the rivet studs. Thefirst friction lining unit 12 comprises a plurality of lining-springelements 34 which are bent out of spring sheets. Two friction linings36, 38 are fixedly connected by rivet studs 40 to the radially innerregions of the lining-spring elements 34 which have openings 42 for thepassage of the rivet studs 32. Therefore, the lining-spring elements 34are first fixedly connected to the friction linings 36, 38 and thenriveted to the radial inner region of the first carrier element 20.

The circumferential wall region 44 of the first carrier element isformed integrally with the cup base region 22 from a sheet-metal blankin a forming operation, e.g. a press forming operation such as adeep-drawing operation. The circumferential wall region 44 is shapedsuch that it forms a toothing configuration 46, the teeth of which areopen radially outward and extend with channels formed between them andextending in the direction of the axis of rotation A.

The clutch disk arrangement 10 according to the present invention alsocomprises a second carrier element 48 which is of almost identicalconstruction to the first carrier element 20 but with a slightly largerdiameter. The second carrier element 48 thus also has a cup base region50 in which, once again, there is a plurality of passage openings 52 forrivet studs 54 for attaching the friction lining unit 14 to the secondcarrier element 48. A circumferential wall region 56 of the secondcarrier element 48 is, in turn, constructed with a toothingconfiguration 55 having teeth which project radially inward. Channelsformed between the teeth of the toothing configuration 55 extendessentially in the direction of the axis of rotation A. A stated above,the diameter of the first carrier element 20 is smaller than thediameter of the second carrier element 48 such that when the secondcarrier element 48 is pushed axially onto the first carrier element 20,the two toothing configurations 46, 55 enter into a meshed engagementwith one another such that they are fixed in terms of relative rotationbut are axially displaceable relative to one another (see FIGS. 1 and2). With respect to the second friction-lining unit 14, it should bestated that this is of essentially identical construction to the firstfriction lining unit 12. Accordingly, the second friction lining unit 14also has a plurality of lining-spring elements 34 which are arranged insuccession in the circumferential direction. Two friction lining 36, 38are riveted to the radially outer region of the lining-spring elements34 and the radial inner region of the lining-spring elements 34 areriveted by rivet studs 40 to the cup base region 50 of the secondcarrier element 48.

It should also be noted that the axial mobility of the first frictionlining unit 12 is achieved by axial movement of the hub 16 on the shaftto which it is connectable. The second friction lining unit 14 isfurther axially movable relative to the first friction lining unit viathe connection between the first and second carrier elements 20, 48.

The clutch disk arrangement 10 according to the embodiment of FIGS. 1-3may be constructed by a simple operation and the function of axialrelative displacement of the first and second friction lining units 12,14 is achieved via the axially movable connection between the first andsecond carrier elements 20, 48. Accordingly, the friction lining units12, 14 may comprise a simple design because the axial displacementfunction is not required to be integrated into the first and secondfriction lining units 12, 14. In particular, the first and secondfriction lining units 12, 14 may be configured as those friction liningunits which are used with conventional single-disk clutches. As statedabove, the function of the lining-spring elements and the function ofallowing axial displacement are separated. Accordingly, each of thesubassemblies may be constructed with the thickness and with thematerial required for the particular function with which the subassemblyis associated. Accordingly, the first and second carrier elements may beobtained by forming sheet metal which furthermore contributes toconstruction of the inventive clutch disk arrangement at reasonablecost.

It should further be noted that an embodiment of this kind may be usednot only with twin-disk clutches but also with a multi-disk clutch,which require more than two friction lining units. It will beappreciated that introducing the toothing configuration 54 into thesecond carrier part 48 during a forming operation produces a toothingconfiguration 58 on the radial outward facing side of thecircumferential wall region 56. The toothing configuration 58 may beused to support another friction lining unit in a manner which preventsrelative rotation and allows axial movement. Regarding the constructionof a friction lining unit that is arrangeable on the toothingconfiguration 58, attention is drawn to the following description of theembodiment shown in FIGS. 4 to 6. It is also possible for a plurality ofsuch additional friction lining units to be provided. For example, theregion of overlap between the first and second carrier elements 20, 48may be made shorter, thereby allowing the toothing configuration 46 ofthe first carrier element 20 also to accept another friction liningunit, which is then axially movable both relative to the first frictionlining unit 12 and to the friction lining unit 14.

Attention is also drawn to the fact that, as shown in FIGS. 7 and 8, atorsional vibration damper may be integrated into the clutch diskarrangement 10 of FIGS. 1-3. In FIG. 7, the first carrier element 20 isconnected to the hub element 16 by a torsional vibration damper 106,rather than by form-fitting or cohesive joining. For this purpose, thecup base region 22 of the first carrier element 20 may, for example,form a central disk element 90 of the torsional vibration damper 106.Cover elements 92, 94 may be arranged so that they rest against bothaxial sides of the central disk element 90. The cover disk elements 92,94 are firmly connected to the hub element 16. Referring to FIG. 7, itis apparent that the radially inner region of the cover disk element 92is welded to the hub element 16 via a weld 118. It is also possible forthe form-fitting contact to take some other form. The two cover diskelements 92, 94 are connected firmly to one another by a plurality ofrivet studs or the like 104 distributed in the circumferentialdirection. The rivet studs 104 may pass through openings (not shown) inthe cup base region 22 to form a limit to the angle of rotation of thetorsional vibration damper 106.

In the embodiment of FIG. 7, the central disk element 90 is otherwisenot firmly connected directly to the hub element 16. Accordingly, thetwo cover disk elements 92, 94 and the cup base region 22 (i.e., centraldisk element 90) may comprise respective spring apertures 96, 98, 100,on which are supported in the circumferential direction respectivedamper springs 102 which permit a rotational movement of the cup baseregion 22 relative to the cover disk elements 92, 94 within a limitedangle of rotation. By means of a support ring 108 of approximatelyL-shaped cross-sectional profile, the cup base region 22 is, on the onehand, supported in the radial direction, in its radially inner portion,on the hub element 16 and supported in the axial direction on the coverdisk element 94. A friction ring 110 may be positioned on the otheraxial side of the cup base region 22, this friction ring 110 beingpressed against the base region 22 by a spring 112, e.g. diaphragmspring supported against the cover disk element 94. Projections 114 maybe formed on the friction ring 110 which engage corresponding cutouts116 in the cover disk element 94. Accordingly, the friction ring 110 ismovable within a predetermined circumferential range relative to thecover disk element 94. The frictional effect which arises between thefriction ring 110 and the cup base region 22 may then be delayed, i.e.may start only after a predetermined angle of relative rotation has beenexceeded. Up to that point, there is a frictional effect between thefriction ring 110 and the spring 112 and/or the spring 112 and the coverdisk element 94. The support ring 108 can also be formed from a materialwhich contributes to increasing the friction force.

FIG. 8 shows an alternate embodiment of the clutch disk arrangement ofFIG. 7 in which the central disk 90 and the support ring 108 are fixedlyconnected to the hub 16 via a weld 118. In this embodiment, the coverdisks 92, 94 are rotatable about the hub element 16 and the firstcarrier element 20 is connected to the cover disks 92, 94. The coverdisk 92 is urged against the support ring 108 by the urgency of thespring 112 arranged between the friction ring 110 and the cover disk 94.The remainder of the configuration of FIG. 8 is the same as that shownand described in FIG. 7.

It should be pointed out that the torsional vibration damper 106 ofFIGS. 7 and 8 may comprise any type of torsional vibration damper. Inparticular, the torsional vibration damper 106 may comprise a pluralityof the springs 102 arranged in series and these springs are supportedagainst one another via respective sliding shoes or the like. Thetorsional vibration damper 106 may also comprise a multi-stage damperwith an idle damping section and a load damping section, as known per sefor clutch disks. It is also possible to use the cup base region 22 asone of the cover-disk elements and to arrange at an axial distance fromit another cover disk element, which is firmly connected to the carrierelement 20. Between the cover disk elements, a central disk element isconnected firmly to the hub element 16.

Referring now to FIGS. 4 to 6, another embodiment of a clutch diskarrangement according to the invention will be described. Componentswhich correspond in terms of construction or function to componentsdescribed above are denoted by the same reference numeral with theaddition of suffix “a”.

The embodiment of the clutch disk arrangement 10 a of FIGS. 4-6comprises a single carrier element 20 a which is firmly connected to thehub element 16 a. This carrier element 20 a once again has anessentially cup-shaped configuration with an opening 24 a for attachmentto the hub element 16 a formed in a cup base region 22 a of the carrierelement 20 a. The circumferential wall region 44 a of the cup-shapedcarrier element 20 a once again has a toothing configuration 46 aprovided therein during formation of the carrier element 20 a. The axialextent of the toothing configuration 46 a is greater than the axialextent of the toothing configurations 46, 55 of FIGS. 1-3. Each of thefirst and second friction lining units 12 a, 14 a comprises a liningcarrier part 60 a of annular design. Referring to FIG. 6, the radiallyouter region of the lining carrier part 60 a comprises respective liningsprings 62 a to which the friction linings 36 a, 38 a are fixed byriveting or adhesive bonding. The radially inner region of the liningcarrier element 60 a has a plurality of projections 64 a which followone another in the circumferential direction and together form atoothing configuration 65 a which is complementary to the toothingconfiguration 46 a of the carrier element 20 a. These two toothingconfigurations 46 a, 66 a may be brought into meshed engagement with oneanother by pushing one axially onto the other. Accordingly, the firstand second friction lining units 12 a, 14 a are coupled to the carrierelement 20 a such that they are fixed with respect to rotation andaxially movable relative to the carrier element 20 a.

To reduce the surface pressure on the contact areas of first and secondfriction lining units 12 a, 14 a in the region of the projections 64 a,tab-like extensions 68 a, 70 a are bent out of both circumferential endsof the projections 64 a. These tab-like extensions 68 a, 70 a come torest against the side faces 72 a, 74 a between each adjacent pair of theteeth 76 a of the toothing configuration 46 a.

The cup base region 22 a of the carrier element 20 a has a raisedportion 80 a in the radial inner area of the cup base region 22 a. Thatis, the cup base region 22 a is arched toward the open end of the spaceformed by the cup base region 22 a and the circumferential wall area 44a of the carrier element 20 a (see FIG. 5). Accordingly, the first andsecond friction lining units 12 a, 14 a may be positioned to assume anapproximately symmetrical position relative to the hub element 16 a inthe direction of the axis of rotation A, thereby enabling very uniformpower transmission to be achieved here. Furthermore, the hub element 16a may be formed with a shorter axial length than the hub element 16 ofthe embodiment in FIGS. 1 to 3. The shorter axial length of the hub 16 ais allowed because, in the embodiment in accordance with FIGS. 1 to 3,the axial displaceability of the friction lining unit connected to thefirst carrier element which is fixed on the hub element is achieved byvirtue of the fact that the hub element is axially displaceable on theshaft coupled to the latter in a manner which prevents relativerotation. However, in the embodiment in accordance with FIGS. 4 to 6,the axial displaceability of all friction lining units 12 a, 14 a isobtained solely by the projections 64 a which engage in the toothingconfiguration 46 a, whereas the hub element 16 a does not have to beaxially displaceable on the associated shaft and may, for example, beaxially fixed thereon.

The embodiment in accordance with FIGS. 4 to 6 has reduced number ofcomponents. Furthermore, the carrier element 20 a may be formed atextremely reasonable cost in a forming operation, e.g. a deepdrawingoperation from a sheet-metal blank. Accordingly, the embodiment of FIGS.4-6 is particularly simple to assemble and costs are minimized becausethe carrier element is simple to produce.

It should be pointed out that the individual lining-spring elementsillustrated in the embodiment in accordance with FIGS. 1 to 3 may beused in the embodiment according to FIGS. 4-6, in which case they shouldeach bear at least one of the projections. Similarly, the use of anintegrally formed lining carrier element such as that shown in FIGS. 4to 6 may be used in the embodiment in FIGS. 1 to 3. In the embodiment inaccordance with FIGS. 4 to 6, it is furthermore also possible for thecarrier element 20 a to be coupled to the hub element 16 a with theinterposition of a torsional vibration damping function, as has beendescribed above by way of example. This means that the base region 22 acan form a subregion, i.e., a central disk or cover disk, of a torsionalvibration damper as shown in FIGS. 9 and 10, the torsional vibrationdamper 106 in FIGS. 9 and 10 being similar to the torsional vibrationdamper 106 discussed above with reference to FIGS. 7 and 8.

Thus, while there have shown and described and pointed out fundamentalnovel features of the invention as applied to a preferred embodimentthereof, it will be understood that various omissions and substitutionsand changes in the form and details of the devices illustrated, and intheir operation, may be made by those skilled in the art withoutdeparting from the spirit of the invention. For example, it is expresslyintended that all combinations of those elements which performsubstantially the same function in substantially the same way to achievethe same results are within the scope of the invention. Moreover, itshould be recognized that structures and/or elements shown and describedin connection with any disclosed form or embodiment of the invention maybe incorporated in any other disclosed or described or suggested form orembodiment as a general matter of design choice. It is the intention,therefore, to be limited only as indicated by the scope of the claimsappended hereto.

I claim:
 1. A clutch disk arrangement for a multi-disk clutch,comprising: a hub element fixedly connectable with respect to rotationabout an axis of rotation to a shaft; a carrier arrangement comprising acarrier element fixedly connectable with respect to rotation relative tosaid hub and having a cup-shaped design having a cup base region and acircumferential wall area; at least two friction lining units connectedto said carrier so that said at least two friction disks are fixed withrespect to rotation relative and axially movable relative to saidcarrier element; and a torsional vibration damper operatively arrangedbetween said carrier element and said hub element.
 2. The clutch diskarrangement of claim 1, further comprising an engagement formation onsaid circumferential wall region of said carrier element and respectivecounterengagement formations arranged on each of said at least twofriction lining units for engaging said engagement formation so thatsaid at least two friction lining units are fixed with respect torotation and axially movable relative to said carrier element.
 3. Theclutch disk arrangement of claim 2, wherein said engagement formationcomprises an external toothing extending longitudinally along thedirection of said axis of rotation.
 4. The clutch disk arrangement ofclaim 2, wherein said carrier element comprises a sheet-metal blankformed via a press forming operation.
 5. The clutch disk arrangement ofclaim 2, wherein each of said friction lining units comprises at leastone lining carrier comprising one part of said counterengagementformation.
 6. The clutch disk arrangement as claimed in claim 1, whereinsaid torsional vibration damper comprises central disk element formed bya base region of said carrier element, a cover disk element arranged onsaid hub element on each side of said central disk element, and at leastone damping element operatively arranged between said central diskelement and said cover disk elements.
 7. A clutch disk arrangement for amulti-disk clutch, comprising: a hub element fixedly connectable withrespect to rotation about an axis of rotation to a shall; a carrierarrangement comprising a carrier element fixedly connectable withrespect to rotation relative to said hub and having a cup-shaped designhaving a cup base region and a circumferential wall area; at least twofriction lining units connected to said carrier so that said at leasttwo friction disks are fixed with respect to rotation relative andaxially movable relative to said carrier element; and an engagementformation on said circumferential wall region of said carrier elementand respective counterengagement formations arranged on each of said atleast two friction lining units for engaging said engagement formationso that said at least two friction lining units are fixed with respectto rotation and axially movable relative to said carrier element,wherein each of said friction lining units comprises at least one liningcarrier comprising one part of said counterengagement formation, andsaid one part of said counterengagement formation comprises at least oneengagement projection arranged on said at least one lining carrier. 8.The clutch disk arrangement of claim 7, further comprising a tab-likeextension arranged on each of said at least one engagement projection,wherein at least one contact surface of said counterengagement formationis formed on said at least one engagement projection by bending saidtab-like extension.
 9. The clutch disk arrangement of claim 7, whereinsaid engagement formation comprises an external toothing extendinglongitudinally along the direction of said axis of rotation.
 10. Theclutch disk arrangement of claim 7, wherein said carrier elementcomprises a sheet-metal blank formed via a press forming operation. 11.The clutch disk arrangement of claim 7, wherein each of said frictionlining units comprises at least one lining carrier comprising one partof said counterengagement formation.